US9091326B2 - Air bleeding valve for hydraulic tensioner of an engine and hydraulic tensioner incorporating same - Google Patents

Air bleeding valve for hydraulic tensioner of an engine and hydraulic tensioner incorporating same Download PDF

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Publication number
US9091326B2
US9091326B2 US13/425,482 US201213425482A US9091326B2 US 9091326 B2 US9091326 B2 US 9091326B2 US 201213425482 A US201213425482 A US 201213425482A US 9091326 B2 US9091326 B2 US 9091326B2
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Prior art keywords
air bleeding
hydraulic tensioner
valve element
valve
valve body
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US13/425,482
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US20120252616A1 (en
Inventor
Yuichi Tawarada
Yoshiaki Tsukada
Osamu Emizu
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Honda Motor Co Ltd
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Honda Motor Co Ltd
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Assigned to HONDA MOTOR CO., LTD. reassignment HONDA MOTOR CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: EMIZU, OSAMU, TAWARADA, YUICHI, TSUKADA, YOSHIAKI
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes or chains 
    • F16H7/0848—Means for varying tension of belts, ropes or chains  with means for impeding reverse motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/04—Special measures taken in connection with the properties of the fluid
    • F15B21/044—Removal or measurement of undissolved gas, e.g. de-aeration, venting or bleeding
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes or chains 
    • F16H2007/0802—Actuators for final output members
    • F16H2007/0806—Compression coil springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes or chains 
    • F16H2007/0802—Actuators for final output members
    • F16H2007/0812—Fluid pressure
    • F16H2007/0814—Fluid pressure with valves opening on surplus pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes or chains 
    • F16H2007/0802—Actuators for final output members
    • F16H2007/0812—Fluid pressure
    • F16H2007/0817—Fluid pressure with means for venting unwanted gas
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes or chains 
    • F16H7/0848—Means for varying tension of belts, ropes or chains  with means for impeding reverse motion
    • F16H2007/0859—Check valves
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7837—Direct response valves [i.e., check valve type]

Definitions

  • the present invention relates to an air bleeding valve for a hydraulic tensioner of an internal combustion engine for applying a proper tension to an endless transmitting member such as an endless chain and an endless belt of power transmission in a valve train for the engine. More particularly, the present invention relates to an air bleeding valve which selectively removes air and suppresses removal of oil in a hydraulic circuit of the hydraulic tensioner, and to a hydraulic tensioner incorporating the same.
  • An internal combustion engine mounted on a vehicle such as a motorcycle is provided with a hydraulic tensioner for pushing an endless transmitting member for driving a camshaft in a valve train, so as to prevent fluttering of the endless transmitting member during the operation of the engine.
  • the spherical valve element is used in the air bleeding valve. Accordingly, when the volume of a valve chamber is increased to remove a large amount of air in a short period of time, the spherical valve element in the valve chamber is unstably moved in the valve chamber to incur vibrations, causing the turbulence of air to be removed. Further, the amount of air to be removed cannot be increased against expectation.
  • oil from the hydraulic circuit is also removed during the removal of air, so that the load on a hydraulic pump is not reduced, resulting in poor fuel economy.
  • the present invention is an improvement over the existing air bleeding valve for the hydraulic tensioner that overcomes the above problems. Accordingly, it is one of the objects of the present invention to provide an air bleeding valve which can selectively remove air in a hydraulic circuit while suppressing the removal of oil in the hydraulic circuit in the initial stage of a starting operation of an internal combustion engine, and which can remove the air efficiently in a short period of time.
  • the present invention provides an air bleeding valve for a hydraulic tensioner having a valve element for removing air from oil contained in a hydraulic circuit of the hydraulic tensioner and for suppressing the removal of the oil, characterized in that an air bleeding valve body is fitted in an air bleeding valve accommodating hole of the hydraulic tensioner; a circumferential groove having a rectangular cross section is formed on the outer circumferential surface of the air bleeding valve body; and the valve element includes an annular valve element having a rectangular cross section fitted in the circumferential groove so as to be movable in an axial direction parallel to the axis of the annular valve element and displaceable in a radial direction toward and away from the axis of the annular valve element.
  • the present invention according to a second aspect thereof, in addition to the first aspect, is characterized in that when an oil pressure is applied to the annular valve element, one end surface of the annular valve element comes into close contact with one side surface of the circumferential groove having a rectangular cross section.
  • the present invention according to a third aspect thereof, in addition to one of the first and second aspects, is characterized in that the annular valve element is formed with a cut portion for allowing elastic deformation of the annular valve element in the radial direction.
  • the present invention according to a fourth aspect thereof, in addition to the third aspect, is characterized in that the cut portion of the annular valve element includes a pair of first cut portions extending axially from the opposite end surfaces of the annular valve element at circumferentially spaced positions to the axially middle position between the opposite end surfaces of the annular valve element and a second cut portion extending circumferentially parallel to the opposite end surfaces of the annular valve element so as to connect the axially inner ends of the first cut portions.
  • the present invention according to a fifth aspect thereof, in addition to the third aspect, is characterized in that the cut portion of the annular valve element includes an inclined cut surface extending from one end surface to the other end surface of the annular valve element so as to be inclined with respect to the axis of the annular valve element.
  • the present invention according to a sixth aspect thereof, in addition to one of the first through fifth aspects, is characterized in that the air bleeding valve body is slidably fitted in the air bleeding valve accommodating hole of the hydraulic tensioner.
  • the present invention according to a seventh aspect thereof, in addition to the sixth aspect, is characterized in that the air bleeding valve body includes an upstream valve body and a downstream valve body; the upstream valve body is slidably inserted in the air bleeding valve accommodating hole of the hydraulic tensioner; the downstream valve body is fixedly mounted in the air bleeding valve accommodating hole such that a spacing is defined between the downstream end surface of the upstream valve body and the upstream end surface of the downstream valve body; and a spring is interposed between the upstream valve body and the downstream valve body for biasing the upstream valve body toward the upstream side.
  • the present invention according to a eighth aspect thereof, in addition the seventh aspect, is characterized in that at least a portion of the spring is fitted in an air bleeding hole formed in the downstream valve body, and the spring includes a coil spring.
  • the present invention according to a ninth aspect thereof, in addition to one of the first through fifth aspects, is characterized in that the air bleeding valve body is fixedly fitted in the air bleeding valve accommodating hole of the hydraulic tensioner.
  • the present invention according to a tenth aspect thereof, in addition to one of the first through ninth aspects, is characterized in that the air bleeding valve body is formed with a central hole located upstream of the circumferential groove and extending axially from the center of the end surface toward the downstream side and a plurality of radial holes extending radially from the downstream end of the central hole and equally spaced in the circumferential direction.
  • the present invention according to an eleventh aspect thereof, in addition to one of the first through tenth aspects, is characterized in that the air bleeding valve body is formed with an air bleeding hole located downstream of the circumferential groove and extending axially so as to communicate with the outside of a tensioner body of the hydraulic tensioner and an air bleeding passage extending radially from the outer circumference of the air bleeding valve body to the air bleeding hole.
  • the present invention according to a twelfth aspect thereof, in addition to one of the first through eleventh aspects, is characterized in that when the hydraulic tensioner is mounted on an internal combustion engine, the upper end of the air bleeding valve accommodating hole is higher in level than a plunger accommodating hole for accommodating a plunger and a pressure holding valve accommodating hole for accommodating a pressure holding valve.
  • the air in a mixture of air and oil is easily passed through the gap between the inner surface (the side surfaces and bottom surface) of the circumferential groove having a rectangular cross section and the side surface (the end surfaces and inner circumferential surface) of the annular valve element having a rectangular cross section because the air has low viscosity, thereby removing the air from the hydraulic circuit.
  • the oil having high viscosity is not allowed to pass through this gap, thereby suppressing the removal of oil from the hydraulic circuit. Accordingly, the air can be efficiently and selectively removed from the oil in the hydraulic circuit, thereby maintaining the function of the hydraulic tensioner at a high level.
  • the annular valve element having a rectangular cross section is fitted in the circumferential groove having a rectangular cross section. Accordingly, the annular valve element can be held stably in the circumferential groove, thereby suppressing the vibrations of the annular valve element.
  • the annular valve element having a rectangular cross section is brought into close contact with the circumferential groove having a rectangular cross section by the oil pressure in the operational condition of the hydraulic tensioner, thereby suppressing the removal of the oil.
  • the removal of the air can be smoothly performed.
  • the amount of air to be removed can be increased with a high level of oil sealability being maintained.
  • the annular valve element having elasticity can be easily fitted into the circumferential groove of the air bleeding valve body without damage. Further, the outer circumferential surface of the annular valve element can be brought into close contact with the inner circumferential surface of the air bleeding valve accommodating hole by the elasticity of the annular valve element, thereby further suppressing the removal of oil and ensuring the sealability.
  • the facing cut surfaces forming the second cut portion extending in the circumferential direction of the annular valve element are kept in close contact with each other, thereby eliminating the leakage of oil.
  • the facing cut surfaces forming the inclined cut surface of the annular valve element are kept in close contact with each other, thereby eliminating the leakage of oil.
  • the air bleeding valve body is slidably fitted in the air bleeding valve accommodating hole. Accordingly, the annular valve element having a rectangular cross section is axially slid by the sliding operation of the air bleeding valve body, so that foreign matter sticking to the inner circumferential surface of the air bleeding valve accommodating hole can be scraped off by the sliding motion of the annular valve element.
  • the air bleeding valve body is reciprocatably slid in the air bleeding valve accommodating hole of the hydraulic tensioner, thereby scraping off the foreign matter sticking to the inner circumferential surface of the air bleeding valve accommodating hole.
  • the channel resistance of the air bleeding hole in the downstream valve body can be increased by the coil spring, thereby further suppressing the leakage of oil.
  • any lid member for preventing the air bleeding valve body from falling out of the air bleeding valve accommodating hole of the hydraulic tensioner is not necessary, thereby simplifying the structure and attaining a cost reduction.
  • a mixture of air and oil introduced into the central hole from the oil introducing side toward the oil exiting side of the air bleeding valve body can be equally dispersed through the plural radial holes to the inner circumferential surface of the air bleeding valve accommodating hole of the air tensioner.
  • the mixture of air and oil can be uniformly dispersed to the entire circumference of the gap formed between the inner circumferential surface of the air bleeding valve accommodating hole of the air tensioner and the outer circumferential surface of the air bleeding valve body, so that only the air can be uniformly removed without radial vibrations of the air bleeding valve body.
  • the mixture of air and small amount of oil possibly passed through the circumferential groove of the air bleeding valve body flows through a downstream passage having a large channel resistance, so that the leakage of oil can be reduced.
  • the upper end of the air bleeding valve accommodating hole is higher in level than the plunger accommodating hole and the pressure holding valve accommodating hole, so that air in the plunger and the pressure holding valve can be smoothly removed.
  • FIG. 1 shows a condition where a hydraulic tensioner having an air bleeding valve according to an illustrative embodiment of the present invention is applied to a timing chain constituting a transmitting mechanism of a valve train in a four-stroke cycle DOHC internal combustion engine mounted on a motorcycle.
  • FIG. 2 shows a cap constituting the hydraulic tensioner as viewed in the direction of the arrow II in FIG. 1 .
  • FIG. 3 is a rear view of a tensioner body constituting the hydraulic tensioner as viewed in the direction of the arrow II in FIG. 1 .
  • FIG. 4 is a longitudinal sectional view taken along the line IV-IV in FIG. 2 .
  • FIG. 5 is a longitudinal sectional view similar to FIG. 4 , showing a condition where a plunger projects frontward from a tensioner body and a tensioner mounting portion of a cylinder head.
  • FIG. 6 is a longitudinal sectional view of the hydraulic tensioner taken along the line VI-VI in FIG. 2 .
  • FIG. 7 is an exploded longitudinal sectional view of a check valve and a relief valve in the hydraulic tensioner.
  • FIG. 8 is an exploded longitudinal sectional view of the air bleeding valve and a pressure holding valve in the hydraulic tensioner in the condition where the check valve and the relief valve are mounted in a valve holder and the air bleeding valve is mounted to the tensioner body.
  • FIG. 9 is an enlarged longitudinal sectional view of the air bleeding valve of the hydraulic tensioner.
  • FIG. 10 is a longitudinal sectional view similar to FIG. 9 , showing a condition where air is passed through the air bleeding valve.
  • FIG. 11 is a cross section taken along the line XI-XI in FIG. 9 .
  • FIG. 12 is an enlarged view of an essential part in FIG. 9 .
  • FIG. 13 is an enlarged view of an essential part in FIG. 10 .
  • FIG. 14 is a plan view showing an embodiment of an annular valve element having a flat cut portion and constituting the air bleeding valve according to the illustrative embodiment of the present invention.
  • FIG. 15 is a cross section taken along the line XV-XV in FIG. 14 .
  • FIG. 16 is a plan view of an annular valve element according to the sixth aspect of the air bleeding valve of the present invention.
  • FIG. 17 is a cross section taken along the line XVII-XVII in FIG. 16 .
  • FIG. 18 is a plan view of an annular valve element according to the seventh aspect of the air bleeding valve of the present invention.
  • FIG. 19 is a cross section taken along the line XIX-XIX in FIG. 18 .
  • FIG. 20 is a longitudinal sectional view of an air bleeding valve according to the fourth aspect of the present invention.
  • FIG. 21 is an enlarged sectional view of the air bleeding valve shown in FIG. 20 .
  • FIG. 22 is a cross section taken along the line XXII-XXII in FIG. 21 .
  • Describe below is an air bleeding valve 30 provided in a hydraulic tensioner 0 according to an illustrative embodiment of the present invention with reference to FIGS. 1 to 15 .
  • FIG. 1 is a right side view of an essential part showing a condition where an internal combustion engine 3 having the hydraulic tensioner 0 is mounted on a body frame 1 of a motorcycle (or a road vehicle such as an automobile).
  • front, rear, upper, lower, right, and left mean the directions with respect to the running direction of the vehicle.
  • front and rear sides of the vehicle are the same as the right and left sides of the drawing, respectively
  • the upper and lower sides of the vehicle are the same as the upper and lower sides of the drawing, respectively
  • the right and left sides of the vehicle are the same as the front and back sides of the sheet of the drawing, respectively.
  • the internal combustion engine 3 of a four-stroke cycle DOHC type has the hydraulic tensioner 0 .
  • the engine 3 is mounted on a motorcycle. More specifically, the front portion of the body frame 1 of the motorcycle is provided with a hanger 2 , and the engine 3 is provided with two projecting bosses 8 . The engine 3 is mounted through the bosses 8 to the hanger 2 and the rear portion of the body frame 1 .
  • the engine 3 has a crankcase 4 , a cylinder block 5 mounted on the upper end of the crankcase 4 , a cylinder head 6 mounted on the upper end of the cylinder block 5 , and a head cover 7 mounted on the upper end of the cylinder head 6 .
  • the crankcase 4 , the cylinder block 5 , the cylinder head 6 , and the head cover 7 are joined together by a suitable joining means such as bolts (not shown).
  • a crankshaft 9 is rotatably supported between the crankcase 4 and the cylinder block 5 .
  • a drive sprocket 10 is fixedly mounted on the crankshaft 9 .
  • a pair of camshafts 11 is rotatably supported to the cylinder head 6 , and a pair of driven sprockets 12 is fixedly mounted on the pair of camshafts 11 , respectively, in the cylinder head 6 and the head cover 7 .
  • An endless timing chain 13 is wrapped among the drive sprocket 10 and the two driven sprockets 12 .
  • the cylinder block 5 is formed with a plurality of cylinder holes (not shown), and a piston (not shown) is vertically slidably fitted in each cylinder hole.
  • the crankshaft 9 is rotatably driven in the clockwise direction as viewed in FIG. 1 by the reciprocating motion of each piston. Torque of the crankshaft 9 is transmitted through the drive sprocket 10 , the endless timing chain 13 , and the two driven sprockets 12 to the two camshafts 11 , thereby driving intake and exhaust valves (not shown) to open and close these valves.
  • the plural cylinder holes formed in the cylinder block 5 of the engine 3 are arranged in the lateral direction of the vehicle.
  • fuel in a combustion chamber is burned once every two revolutions of the crankshaft 9 , and each piston is intermittently pushed toward the crankshaft 9 by the pressure of a combustion gas.
  • a running resistance changes due to the unevenness on a road surface during running of the motorcycle.
  • the tension of the endless timing chain 13 varies to easily cause fluttering of the endless timing chain 13 in the longitudinal direction of the vehicle.
  • a chain guide 14 is provided so as to come into contact with a front portion of the endless timing chain 13 on the tension side, i.e., on the right side as viewed in FIG. 1 .
  • a tensioner slipper 15 is provided so as to come into contact with a rear portion of the endless timing chain 13 on the slack side, i.e., on the left side as viewed in FIG. 1 .
  • the hydraulic tensioner 0 is mounted on the cylinder head 6 at a position on the rear side of the tensioner slipper 15 so as to be disposed adjacent to the tensioner slipper 15 .
  • the hydraulic tensioner 0 has a specific structure and characteristics to be hereinafter described in detail. Owing to the excellent characteristics of the hydraulic tensioner 0 , the fluttering of the rear portion of the endless timing chain 13 on the slack side can be efficiently suppressed.
  • the hydraulic tensioner 0 shown in FIG. 1 has a housing including a tensioner body 20 and a cap 21 .
  • the cap 21 is formed with a pair of right and left bolt insertion holes 21 a .
  • FIG. 3 which is a rear view of the tensioner body 20 as viewed in the direction of the arrow II in FIG. 1 , the tensioner body 20 is formed with a pair of right and left bolt insertion holes 20 b respectively aligned to the right and left bolt insertion holes 21 a of the cap 21 .
  • Two bolts (not shown) are inserted through the two bolt insertion holes 21 a of the cap 21 and the two bolt insertion holes 20 b of the tensioner body 20 and threadedly engaged with a tensioner mounting portion 6 a formed at the rear portion of the cylinder head 6 .
  • the hydraulic tensioner 0 is fixedly mounted on the cylinder head 6 .
  • a packing fitting groove 20 d is formed on the rear end surface 20 c of the tensioner body 20 so as to surround a plunger accommodating hole 20 a , and an endless packing 20 e is fitted in the packing fitting groove 20 d .
  • a recess 21 c is formed on the front end surface 21 b of the cap 21 , and an oil storing chamber 28 is defined by the recess 21 c of the cap 21 and the rear end surface 20 c of the tensioner body 20 .
  • a base end portion 22 a of a valve holder 22 shown in FIG. 7 is fixedly fitted in the rear portion of the plunger accommodating hole 20 a of the tensioner body 20 as shown in FIGS. 4 to 6 .
  • a plunger 23 is slidably fitted in the plunger accommodating hole 20 a of the tensioner body 20 .
  • a high oil pressure chamber 31 is defined in the plunger 23 , and a coil spring 24 as biasing means is provided in the plunger accommodating hole 20 a and the high oil pressure chamber 31 so that the opposite ends of the coil spring 24 abuts against the shoulder front end surface 22 b of the base end portion 22 a of the valve holder 22 and the inner surface 23 b of the front end portion 23 a of the plunger 23 .
  • the plunger 23 is normally biased by the coil spring 24 so as to project frontward from the tensioner mounting portion 6 a of the cylinder head 6 as shown in FIG. 5 . Further, a contact portion 23 c adapted to come into contact with the tensioner slipper 15 is fixedly mounted on the front end portion 23 a of the plunger 23 .
  • the base end portion 22 a of the valve holder 22 is formed with a valve accommodating hole 22 c (see FIG. 7 ), and a valve guide 25 a of a check valve 25 is fixedly fitted in the front portion of the valve accommodating hole 22 c .
  • a check valve coil spring 25 b and a spherical valve element 25 c are fitted in the valve guide 25 a from the rear end thereof.
  • a valve element 26 a of a relief valve 26 is slidably fitted in the valve accommodating hole 22 c of the valve holder 22 .
  • a valve chamber 26 b is formed in the valve element 26 a .
  • a relief valve seat 27 is provided in the oil storing chamber 28 (see FIGS. 4 and 5 ) so as to be disposed adjacent to the cap 21 .
  • a relief valve coil spring 26 d is provided in the valve chamber 26 b so that the opposite ends of the relief valve coil spring 26 d abut against the relief valve seat 27 and the front end portion 26 c of the valve element 26 a of the relief valve 26 .
  • the oil storing chamber 28 is in communication with the high oil pressure chamber 31 through an opening 27 a of the relief valve seat 27 , the relief valve 26 , and the check valve 25 .
  • a pressure holding valve 29 will now be described.
  • a pressure holding valve accommodating hole 20 f is formed in the tensioner body 20 at a position on the right lower side of the plunger accommodating hole 20 a so as to extend parallel to the plunger accommodating hole 20 a (see FIGS. 4 and 5 ).
  • the rear end of the pressure holding valve accommodating hole 20 f opens to the oil storing chamber 28 surrounded by the endless packing 20 e.
  • a spring seat 29 a Prior to mounting the cap 21 to the tensioner body 20 , a spring seat 29 a , a closing coil spring 29 b , and a valve element 29 c constituting the pressure holding valve 29 are fitted in this order into the pressure holding valve accommodating hole 20 f of the tensioner body 20 from its rear opening as shown in FIG. 8 .
  • the rear portion of the valve element 29 c is formed as a small-diameter cylindrical portion 29 d .
  • the valve element 29 c is normally biased rearward by the closing coil spring 29 b , so that the rear end surface 29 e of the small-diameter cylindrical portion 29 d of the valve element 29 c abuts against the front end surface 21 b of the cap 21 .
  • a communication port 20 g of the tensioner body 20 communicating with a relief valve port 22 e of the valve holder 22 is closed by the valve element 29 c.
  • the relief valve port 22 e formed in the valve holder 22 is composed of a circumferential groove 22 e 1 formed on the outer circumferential surface of the base end portion 22 a and a plurality of radial holes 22 e 2 formed at circumferentially equal intervals so as to extend radially from the bottom of the circumferential groove 22 e 1 toward the center of the valve accommodating hole 22 c.
  • the air bleeding valve 30 will now be described.
  • an air bleeding valve accommodating hole 20 h is formed in the tensioner body 20 at a position on the left upper side of the plunger accommodating hole 20 a so as to extend parallel to the plunger accommodating hole 20 a .
  • the air bleeding valve accommodating hole 20 h has a circular cross section.
  • the upper end of the air bleeding valve accommodating hole 20 h is higher in level than the plunger accommodating hole 20 a and the pressure holding valve accommodating hole 20 f . Accordingly, air in the plunger 23 and the pressure holding valve 29 is smoothly removed through the air bleeding valve accommodating hole 20 h .
  • the rear portion of the air bleeding valve accommodating hole 20 h is in communication with the high oil pressure chamber 31 through an air bleeding passage 20 j.
  • the air bleeding valve 30 has an air bleeding valve body 30 b .
  • the air bleeding valve body 30 b is composed of an upstream valve body 30 b 1 and a downstream valve body 30 b 2 .
  • the upstream valve body 30 b 1 , a coil spring 30 e , and the downstream valve body 30 b 2 are fitted in this order into the air bleeding valve accommodating hole 20 h from its front opening.
  • the downstream valve body 30 b 2 is threadedly engaged with the air bleeding valve accommodating hole 20 h .
  • a pressure change in the high oil pressure chamber 31 is transmitted through the air bleeding passage 20 j to the air bleeding valve accommodating hole 20 h , so that the upstream valve body 30 b 1 is slightly moved in the axial direction.
  • the outer circumference of the upstream valve body 30 b 1 is formed with a circumferential groove 30 c having a rectangular (or square) cross section.
  • An annular valve element 30 d is loosely fitted in the circumferential groove 30 c . That is, the annular valve element 30 d has a width (axial dimension) slightly smaller than the width of the circumferential groove 30 c and a height (radial dimension) slightly smaller than the depth of the circumferential groove 30 c . As shown in FIGS.
  • the annular valve element 30 d is cut along the axis 30 g to form a flat cut portion (slit) 30 h extending in the axial direction, so that the inner diameter of the annular valve element 30 d becomes greater than or equal to the diameter of the circumferential groove 30 c . Accordingly, the annular valve element 30 d is elastically deformed to be fitted into the circumferential groove 30 c.
  • the annular valve element 30 d is formed of metal in this illustrative embodiment.
  • the annular valve element 30 d may be formed of relatively hard synthetic resin.
  • the edge formed between the circumferential surface and each end surface of the annular valve element 30 d is formed as a sharp edge.
  • the upstream valve body 30 b 1 is formed with an air bleeding passage 30 a at a rear portion on the upstream side of the annular valve element 30 d .
  • the air bleeding passage 30 a is composed of a central hole 30 a 1 extending in the axial direction frontward from the center of the rear end surface 30 b 3 of the upstream valve body 30 b 1 (see FIG. 9 ) and four radial holes 30 a 2 extending in the radial direction from the front end of the central hole 30 a 1 and equally spaced in the circumferential direction.
  • the downstream valve body 30 b 2 is also formed with an air bleeding hole 30 i centrally extending in the axial direction. Accordingly, when a pressure change is transmitted through the air bleeding passage 20 j to the upstream valve body 30 b 1 , the upstream valve body 30 b 1 is axially reciprocated by the biasing force of the coil spring 30 e , so that foreign matter contained in the oil and sticking to the inner surface of the air bleeding valve accommodating hole 20 h can be scraped off by the sharp edge formed between the circumferential surface and each end surface of the annular valve element 30 d.
  • the lower portion of the oil storing chamber 28 defined by the recess 21 c of the cap 21 and the rear end surface 20 c of the tensioner body 20 is connected through a tensioner oil passage 32 to a cylinder head oil passage 33 .
  • the tensioner oil passage 32 extends in the tensioner body 20 from the rear portion toward the front portion so as to be inclined downward.
  • the cylinder head oil passage 33 is formed in the tensioner mounting portion 6 a of the cylinder head 6 .
  • the cylinder head oil passage 33 is connected through an oil passage (not shown) formed in the cylinder block 5 and an oil passage 34 formed in the crankcase 4 to an oil filter 35 .
  • the oil filter 35 is connected through an oil passage 36 to a discharge port of an oil pump 37 .
  • the oil pump 37 When the oil pump 37 is operated by the operation of the engine 3 , the oil stored in the bottom portion of the crankcase 4 is pumped up through a strainer 38 to the oil pump 37 .
  • the oil discharged from the oil pump 37 is supplied through the oil passage 36 , the oil filter 37 , the oil passage 34 , the cylinder head oil passage 33 , and the tensioner oil passage 32 to the oil storing chamber 28 .
  • an oil supply passage is formed by the tensioner oil passage 32 connected to the cylinder head oil passage 33 of the cylinder head 6 , the oil storing chamber 28 , the valve chamber 26 b of the relief valve 26 , and a valve hole 26 e formed through the front end portion 26 c of the valve element 26 a of the relief valve 26 .
  • the upstream valve body 30 b 1 fitted in the air bleeding valve accommodating hole 20 h of the tensioner body 20 is axially slidable relative to the downstream valve body 30 b 2 and reciprocated by the biasing force of the coil spring 30 e .
  • a mixture of oil and air is introduced from the high oil pressure chamber 31 through the air bleeding passage 20 j to the gap between the inner surface of the air bleeding valve accommodating hole 20 h and the outer surface of the upstream valve body 30 b 1 .
  • the air in this mixture is passed, because of its low viscosity, through the gap between the inner surface (the side surfaces and bottom surface) of the circumferential groove 30 c and the side surface (the end surfaces and inner circumferential surface) of the annular valve element 30 d as shown in FIG. 12 and next passed through an air bleeding passage (spacing) 30 b 4 formed between the upstream valve body 30 b 1 and the downstream valve body 30 b 2 to the air bleeding hole 30 i as shown in FIG. 9 .
  • the air is finally removed from the air bleeding hole 30 i through an air bleeding hole 6 c formed in the cylinder head 6 as shown in FIGS. 4 and 5 .
  • the oil higher in viscosity than the air is introduced into the gap between the upstream inner surface of the circumferential groove 30 c and the upstream end surface of the annular valve element 30 d .
  • the annular valve element 30 d is pushed toward the downstream side, i.e., toward the front side by the pressure of the oil having a high viscosity.
  • the downstream end surface of the annular valve element 30 d comes into close contact with the downstream inner surface of the circumferential groove 30 c as shown in FIG. 13 , thereby stopping the flow of the air and the oil.
  • the annular valve element 30 d is expanded radially to block the discharge of the oil to the air bleeding hole 30 i.
  • the upstream valve body 30 b 1 When the oil pressure in the high oil pressure chamber 31 is reduced, the upstream valve body 30 b 1 is moved rearward by the biasing force of the coil spring 30 e , so that only the air in the air-oil mixture introduced into the air bleeding valve accommodating hole 20 h is selectively removed from the air bleeding hole 30 i.
  • pressure change in the high pressure oil chamber 31 which receives pressurized fluid from the oil pump 37 , moves the upstream valve body 30 b 1 slightly in the axial direction as well as the annular valve element 30 d , and when the pressure in the high pressure oil chamber 31 is reduced the upstream valve body 30 b 1 and the annular valve element 30 d are moved slightly in the opposite direction by the force of spring 30 e , and the process is repeated with further pressure changes in the high pressure oil chamber 31 .
  • the upstream valve body 30 b 1 is allowed to slightly slide on the inner circumferential surface of the air bleeding valve accommodating hole 20 h . Accordingly, foreign matter sticking to the inner circumferential surface of the air bleeding valve accommodating hole 20 h can be scraped off by the sharp edge formed between the outer circumferential surface and each end surface of the annular valve element 30 d , thereby suppressing the leakage of oil.
  • the upstream valve body 30 b 1 is formed with the central hole 30 a 1 and the plural radial holes 30 a 2 equally spaced in the circumferential direction. Accordingly, the mixture of air and oil can be uniformly dispersed to the entire circumference of the gap formed between the inner circumferential surface of the air bleeding valve accommodating hole 20 h and the outer circumferential surface of the annular valve element 30 d , thereby efficiently performing air bleeding.
  • the annular valve element 30 d having a rectangular cross section is fitted in the circumferential groove 30 c having a rectangular cross section. Accordingly, the annular valve element 30 d can be stably held in the circumferential groove 30 c , thereby suppressing the vibrations of the valve element 30 d.
  • the annular valve element 30 d has the flat cut portion 30 h and is formed of an elastically deformable material. Accordingly, the annular valve element 30 d can be easily fitted into the circumferential groove 30 c of the air bleeding valve body 30 b without damage. Further, the outer circumferential surface of the annular valve element 30 d can be brought into close contact with the inner circumferential surface of the air bleeding valve accommodating hole 20 h by the elasticity of the annular valve element 30 d , thereby further suppressing the removal of oil and ensuring the sealability.
  • the mixture of air and oil possibly passed through the circumferential groove 30 c of the air bleeding valve body 30 b flows through a downstream passage having a large channel resistance, so that the leakage of oil can be reduced.
  • the channel resistance of the air bleeding hole 30 i in the downstream valve body 30 b 2 can be increased by the coil spring 30 e , thereby further suppressing the leakage of oil.
  • the upper end of the air bleeding valve accommodating hole 20 h is higher in level than the plunger accommodating hole 20 a and the pressure holding valve accommodating hole 20 f , so that air in the plunger 23 and the pressure holding valve 29 can be smoothly removed through the air bleeding valve accommodating hole 20 h.
  • FIGS. 16 and 17 show an annular valve element 30 j according to a second illustrative embodiment of the present invention in addition to the annular valve element 30 d according to the illustrative embodiment shown in FIGS. 1 to 15 .
  • the annular valve element 30 j is formed with a stepped cut portion.
  • the stepped cut portion is composed of a pair of first cut portions 30 k extending axially from the opposite end surfaces of the annular valve element 30 j at circumferentially spaced positions to the axially middle position between the opposite end surfaces of the annular valve element 30 j and a second cut portion 30 m circumferentially extending parallel to the opposite end surfaces of the annular valve element 30 j so as to connect the axially inner ends of the first cut portions 30 k.
  • the annular valve element 30 j according to the second illustrative embodiment shown in FIGS. 16 and 17 can exhibit an effect similar to that of the annular valve element 30 d according to the illustrative embodiment shown in FIGS. 1 to 15 .
  • the facing cut surfaces forming the second cut portion 30 m are kept in close contact with each other, thereby eliminating the leakage of oil.
  • annular valve element 30 q can be configured as shown in FIGS. 18 and 19 .
  • the annular valve element 30 q is formed with an inclined cut surface 30 r extending from one end surface to the other end surface of the annular valve element 30 q so as to be inclined with respect to the axis 30 p of the annular valve element 30 q .
  • the annular valve element 30 q can also exhibit an effect similar to that of the annular valve element 30 j shown in FIGS. 16 and 17 . That is, even when the diameter of the annular valve element 30 q is increased, the facing cut surfaces forming the inclined cut surface 30 r are kept in close contact with each other.
  • the air bleeding valve body 30 b is composed of the upstream valve body 30 b 1 and the downstream valve body 30 b 2 separated from each other, and the coil spring 30 e is interposed between the upstream valve body 30 b 1 and the downstream valve body 30 b 2 .
  • an air bleeding valve body 30 s according to a fourth illustrative embodiment shown in FIGS. 20 to 22 is an integral member fixedly fitted in the air bleeding valve accommodating hole 20 h .
  • Four radial holes 30 t as an air bleeding passage and a central hole 30 u as an air bleeding hole extending in the axial direction and connected to the four radial holes 30 t are formed on the downstream side of the air bleeding valve body 30 s.
  • the hydraulic tensioner is largely inclined downward on the front side, and the front end of the air bleeding hole 30 u is connected to the air bleeding hole 6 c formed in the tensioner mounting portion 6 a , so that the air separated from the oil in the air bleeding body 30 s is discharged into the cylinder head.
  • the coil spring 30 e is not required, so that the number of parts can be reduced and the structure of the air bleeding valve can be simplified, thereby attaining a cost reduction.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
US13/425,482 2011-03-31 2012-03-21 Air bleeding valve for hydraulic tensioner of an engine and hydraulic tensioner incorporating same Active 2033-05-11 US9091326B2 (en)

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JP2011-077425 2011-03-31
JP2011077425A JP5725932B2 (ja) 2011-03-31 2011-03-31 油圧テンショナのエア抜き弁

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US8951154B2 (en) * 2011-03-31 2015-02-10 Honda Motor Co., Ltd. Hydraulic tensioner
JP5913040B2 (ja) * 2012-10-09 2016-04-27 株式会社椿本チエイン チェーンテンショナ
JP2017505411A (ja) * 2014-01-28 2017-02-16 ボーグワーナー インコーポレーテッド オリフィス流れ弁
JP6310335B2 (ja) * 2014-02-21 2018-04-11 本田技研工業株式会社 油圧テンショナ装置
KR20180034480A (ko) * 2015-07-28 2018-04-04 보르그워너 인코퍼레이티드 환기부를 갖는 2 피스형 피스톤
US10738860B2 (en) * 2016-09-30 2020-08-11 Borgwarner Inc. Hydraulic tensioner with controllable inlet pressure
JP6806994B2 (ja) * 2016-11-07 2021-01-06 株式会社椿本チエイン テンショナ
JP6795764B2 (ja) * 2017-03-21 2020-12-02 株式会社椿本チエイン テンショナ
JP7208099B2 (ja) * 2019-04-25 2023-01-18 日立造船株式会社 監視システム

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DE102012205137B4 (de) 2017-10-26
JP5725932B2 (ja) 2015-05-27
JP2012211644A (ja) 2012-11-01
US20120252616A1 (en) 2012-10-04
DE102012205137A1 (de) 2012-10-04

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